DE102020119832A1 - Elastomer bushing and elastic bearing for wind turbines - Google Patents

Abstract

The present invention relates to an elastomeric bushing for an elastic bearing of a drive train component of a wind turbine, in particular a gearbox on a housing, such as a machine carrier, of a wind turbine, comprising two half-shells, each made of an elastomer piece with a Shore hardness of more than 85 Shore A are, wherein at least one half-shell has an axial stiffness that varies in the direction of its longitudinal axis.

Description

The present invention relates to an elastomeric bushing for an elastic bearing of a drive train component of a wind turbine. Furthermore, the present invention relates to an elastic bearing, in particular a decoupling bearing, for mounting a drive train component, in particular a transmission, of a wind power plant, in particular on its housing, such as a machine carrier.

In wind turbines, a large amount of torque is transmitted from the engine to the gearbox and from there to the generator. To reduce the dynamic loads on the gearbox and supporting structure, elastic bearings are usually used in the gearbox supports. The elastic mounts have elastic bushings for isolating oscillations and vibrations, which are integrated into the mounting of the drive train and are, for example, part of the loose bearing unit in the drive train. The floating bearing unit consists of four elastic bushes and the roller bearing unit in the gearbox. The elastic bushings are connected to the gearbox via the torque arm (axle bolt) and to the housing or the machine carrier via bearing blocks. On the one hand, the elastic bushings are required to withstand the high and fluctuating forces acting on the bearing, for example due to wind, and on the other hand to be as soft as possible in the longitudinal direction, so that play of the axle bolt is guaranteed.

the end EP 2 516 883 a generic storage is known. With regard to the requirements for generic bearings and their installation situation EP 2 516 883 referred. The bearing includes a clamping bush with an eccentric geometry. The clamping bush consists of two oval half-shells, which are made of rubber and are reinforced or stiffened with metal inserts. Due to the oval geometry, the clamping bushing still has large dimensions in the vertical direction transverse to the longitudinal axis and therefore requires a lot of space. It is also very heavy, which is further increased by the metal inserts. Finally, manufacturing is difficult due to the combination of elastomeric material and metal insert. A further disadvantage is that the adaptation of a desired axial and/or radial stiffness is associated with a great deal of effort, in particular because of the coordination of the elastomer geometry and the metal insert.

It is the object of the present invention to improve the disadvantages of the known prior art, in particular to provide an elastomer bushing and an elastic bearing for wind turbines which is/are lighter in weight, takes up less installation space and/or is more flexible with regard to the axial and/or or radial stiffness is to be adjusted.

This object is solved by the features of the independent claims.

According to this, an elastomeric bushing is provided for an elastic bearing of a drive train component of a wind turbine. For example, it is an elastomeric bushing for an elastic bearing of a gear mechanism on a housing, such as a machine support of a wind turbine. Resilient mounts are used in wind turbines to absorb the dynamic loads acting on the drive train component and housing. Oscillation and/or vibration damping and decoupling can take place by means of the elastomer bushing. With regard to the basic installation situation of the elastomer bushing or the elastic bearing, see EP 2 516 883 referenced, the relevant content of which is incorporated by reference into the present application.

The elastomeric bushing according to the invention comprises two half-shells, each of which is made from a piece of elastomer, in particular monolithic, with a Shore hardness of more than 85 Shore A. The Shore hardness is a material parameter for elastomers and plastics that is specified in the standards DIN EN ISO 868, DIN ISO 7619-1 and ASTM D 2240-00. The half-shells can be made of the same material and/or have the same dimensions. In an assembled state in the elastic mount, the two half-shells can rest on one another at the front to form a particularly cylindrical passage, for example for a fastening part of the drive train component, such as the torque arm or the axle bolt. A wall thickness of the half-shells can be dimensioned significantly smaller than their circumferential extension. The half-shells can have a c-shape or a half-ring shape in cross-section. The selected Shore hardness of the half-shells, in particular of the elastomer piece material, ensures the necessary resilience, whereby, for example, compared to standard rubber-metal elastomer bushings, up to four times higher loads can be absorbed with comparable deformation, while at the same time it is possible to dimension the elastomer bushings significantly smaller. In this respect, a lower component weight, lower component costs and smaller component dimensions can be achieved.

According to the invention, at least one half-shell, in particular both half-shells, have a varying in the direction of their longitudinal axis axial stiffness. For example, the at least one half-shell is designed and/or constructed in such a way that at least two axial sections of the half-shell are formed, which have different axial rigidity. Thus, on the one hand, the considerable load requirements, particularly in the radial direction, can be met and, at the same time, the axial rigidity can be adjusted as a function of the specific requirements. For example, this makes it possible to design the axial rigidity of the elastomeric bushing to be significantly lower than the radial rigidity. In particular, the inventors of the present invention have succeeded in being able to set the axial rigidity independently of the radial rigidity, at least to a certain extent. Due to the flexible design of the axial and radial rigidity of the elastomeric bushing, further savings can be achieved in terms of material expenditure, installation space and thus also costs. In the present case, the axial rigidity can be understood as meaning the resistance of the elastomer bushing, in particular the half-shell, to elastic deformation by an external application of force, in particular in the direction of the longitudinal axis, for example a shearing or stretching load. In the present case, radial rigidity can be understood as meaning the resistance of the elastomer bushing or the half-shells to elastic deformation when a force is applied transversely, in particular radially, to the longitudinal axis. The varying axial rigidity can be achieved, for example, in that at least one half-shell is segmented, in particular having different radial wall thicknesses along the longitudinal axis. Furthermore, it is possible to configure the radial rigidity as a function of the orientation, in which case, for example, the radial rigidity in the horizontal direction can be greater or smaller than the radial rigidity in the vertical direction.

In an exemplary embodiment of the present invention, at least one piece of elastomer comprises polyurethane. For example, it is polyurethane-polyester or polyester-urethane rubber. Urelast is preferably used. The materials mentioned for the elastomer piece have proven to be particularly advantageous, in particular because of the high load capacity, high tensile strength and very good wear behavior. Mainly because of the high load capacity, it is possible to dimension the elastomer bushing smaller. This results in advantages in terms of installation space, material requirements and costs. Urelast is generally a cast elastomer.

According to a further exemplary embodiment of the elastomer bush according to the invention, the half-shells each have a central axis which is oriented concentrically to one another when the half-shells rest on one another and/or in the mounted state in the bearing, in particular in the operating state. Due to the concentric arrangement, there are above all further space advantages. In order to establish different rigidities in different directions, it is no longer necessary to configure the half-shells, for example, as oval or elliptical and/or to arrange them eccentrically to one another in the mounted state in the elastic bearing. In the assembled state, the elastomer piece half-shells essentially form a ring shape, with a particularly cylindrical passage for a fastening part of the drive train component, such as the torque arm or the axle bolt, and an at least approximately round outer circumference, which in the assembled state in the bearing, particularly in the operating state, is contacted by two bearing block parts, in particular is completely surrounded and/or is in particular received in a clamping manner.

In an exemplary development of the elastomeric bushing according to the invention, its radial rigidity transversely to the longitudinal axis is greater than its axial rigidity in the direction of the longitudinal axis. For example, the axial stiffness is less than 10%, in particular less than 5% or less than 2% of the radial stiffness. The specified ratios have proven to be particularly advantageous with regard to the specific requirements in elastic bearings in wind turbines for mounting the drive train component on the housing, in particular the machine carrier, of the wind turbine. When using the elastomer bush in floating bearings, a particularly low axial rigidity is desired. Furthermore, it is possible to configure the radial rigidity as a function of the orientation, in which case, for example, the radial rigidity in the horizontal direction can be greater or smaller than the radial rigidity in the vertical direction. For example, the radial stiffnesses in the different directions can deviate from one another by 5% or by 8% or by more than 10%.

According to a further aspect of the present invention, which can be combined with the preceding aspects and exemplary embodiments, an elastomeric bushing is provided for an elastic bearing of a drive train component of a wind turbine. For example, it is an elastomeric bushing for an elastic bearing of a gear mechanism on a housing, such as a machine support of a wind turbine. Resilient mounts are used in wind turbines to absorb the dynamic loads acting on the drive train component and housing. Oscillation and/or vibration damping and decoupling can take place by means of the elastomer bushing. With regard to the basic installation situation of the elastomer bushing or the elastic bearing, see EP 2 516 883 referenced, the relevant content of which is incorporated by reference into the present application.

The elastomeric bushing according to the invention comprises two half-shells, each of which is made from a piece of elastomer, in particular monolithic, with a Shore hardness of more than 85 Shore A. The Shore hardness is a material parameter for elastomers and plastics that is specified in the standards DIN EN ISO 868, DIN ISO 7619-1 and ASTM D 2240-00. The half-shells can be made of the same material and/or have the same dimensions. In an assembled state in the elastic mount, the two half-shells can rest on one another at the front to form a particularly cylindrical passage, for example for the torque support. A wall thickness of the half-shells can be dimensioned significantly smaller than their circumferential extent. The half-shells can have a c-shape or a half-ring shape in cross-section. The selected Shore hardness of the half-shells, in particular of the elastomer piece material, ensures the necessary resilience, whereby, for example, up to four times higher loads can be absorbed in comparison to the rubber-metal elastomer bushes used as standard, while at the same time it is possible to significantly increase the elastomer bushings to size smaller. In this respect, a lower component weight, lower component costs and smaller component dimensions can be achieved.

According to the further aspect of the invention, at least one half-shell, in particular the half-shell with the varying axial rigidity, has at least two support webs arranged at a distance from one another in the longitudinal direction and/or transversely, in particular perpendicularly, to one another. The support webs protrude from an outer or inner circumference of the half-shell in such a way that an alternative space is formed between each two support webs. The escape space can be a groove or a recess, for example. The support webs arranged on the outer circumference, hereinafter also referred to as outer support webs, are in load-bearing contact with the bearing parts of the elastic bearing surrounding the elastomer piece half-shells on the outside in the mounted state in the bearing, in particular in the operating state. Support webs provided on the inner circumference of the half-shell, also referred to below as inner support webs, come into load-bearing contact with the drive train component, in particular its torque support or axle bolt, in the operating state, i.e. when installed in the bearing Half shells limited implementation is added. Support webs that are arranged at the same axial height of the elastomer bushing with respect to its longitudinal axis and are separated from one another by an escape space, such as a groove or a recess, can be referred to as circumferential support webs. Support webs that are arranged at the same circumferential height of the elastomer bushing with respect to its longitudinal axis and are separated from one another by an escape space, such as a groove or a recess, can be referred to as axial support webs. In this way it is possible, in particular by flexible configuration of the geometry of the elastomeric bushing, to flexibly adjust the spring stiffness of the elastomeric bushing with respect to all spatial axes, in particular in order to be able to react to any load requirements. The inventors of the present invention have found that the axial rigidity as well as the radial rigidity can be adjusted in a targeted manner on the one hand in the horizontal direction and on the other hand in the vertical direction via the support web/evasion space structure of the elastomer bushing.

According to an exemplary development of the elastomeric bushing according to the invention, the support webs are designed to yield to an adjacent escape space on the elastomeric bushing (1) in the longitudinal direction and/or transversely thereto in the event of a load, in particular in the longitudinal direction and/or transversely thereto. In this way it is possible to set the axial rigidity and/or the radial rigidity, for example as a function of the loads to be expected, the dimensioning of the wind turbine and/or the power of the wind turbine. The axial rigidity and/or the radial rigidity can be adjusted, for example, by the dimensioning of the support webs and/or the grooves. In general, it is true that the higher the degree of deflection of the supporting webs into adjacent deflection spaces, the lower the rigidity of the half-shell in this direction.

In a further exemplary embodiment of the elastomeric bushing according to the invention, the supporting webs have a rectangular shape or a conical shape in cross section. For example, it is possible for the support webs to taper, in particular continuously, in the radial direction. A discontinuous taper is also conceivable. The cross-sectional shape of the supporting webs can also be used to adjust their ability to deviate into the adjacent grooves in order to achieve a specific rigidity in this direction.

According to a further exemplary development of the elastomeric bushing according to the invention, at least one support web is segmented in the circumferential direction and/or divided into circumferential sections. The sections of the support webs that are segmented or subdivided in the circumferential direction can be referred to as circumferential support webs. In this case, the at least one support web in the circumferential direction such be segmented or subdivided so that at least 2, 3 or 4 peripheral support webs are formed. The circumferential support webs can extend in the circumferential direction by substantially the same circumferential dimensions. Furthermore, each two adjacent peripheral support webs can be separated from one another in the peripheral direction by a recess which is in particular rectilinear and/or oriented in the longitudinal direction and which forms the escape space. The recesses can also be curved at least in sections.

According to an exemplary development of the elastomeric bushing according to the invention, the peripheral support webs are designed to deviate in the peripheral direction into an adjacent recess in the event of a load, in particular transversely to the longitudinal direction, on the elastomeric bushing. With regard to the recess and the deflection of the peripheral support webs into this, the statements regarding the groove and the deflection of the support webs into this apply in an analogous manner. The segmentation of the supporting webs in the circumferential direction enables an additional adjustment of the rigidity of the elastomeric bushing or the corresponding half-shell in the circumferential direction, in particular independently of the axial rigidity or without significantly influencing the axial rigidity.

In a further exemplary embodiment of the elastomer bush according to the invention, at least one half-shell has an anti-twist device. The anti-rotation lock is set up to prevent rotation of the elastomeric bushing about the axial direction when the elastic bearing is in operation. For example, the anti-twist device is implemented by pinning, gluing, or by a radial projection that interacts with a bearing block part of the bearing. For example, the radial projection is a shoulder that protrudes radially from the outer circumference of the half-shell and is located between the bearing block parts in the installed state in the bearing. For example, the radial projection is clamped by the two bearing block parts. For example, the radial projection can come into positive engagement with at least one bearing block part, so that a relative rotation between the elastomer bushing and the bearing block part is prevented.

According to an exemplary development of the elastomeric bushing according to the invention, the half-shells have a c-shaped cross section. The radial projection can be arranged in the area of an open end of the c-shaped cross section, in other words in the area of an open end section of the half-shell. For example, both half-shells have a radial projection that is in particular of the same design and that can be arranged essentially at the same point on the respective half-shell, so that the radial projections face one another in the operating state, in particular rest on one another and/or are clamped against one another by the bearing block parts.

In a further exemplary embodiment of the present invention, at least one half-shell has a radial rigidity that varies transversely to the longitudinal axis. It has also been found that the radial loads on the elastomeric bushing are not completely evenly distributed in the circumferential direction. The inventors of the present invention have found that there are areas of increased stress. Targeted strengthening in the highly stressed areas and/or targeted relative weakening in the less heavily stressed areas makes it possible to achieve further savings in terms of costs, material and installation space. The intelligent design of the elastomer bushing is supported by the preferred choice of material, which on the one hand ensures flexible production and on the other hand is very resilient.

According to an exemplary development of the elastomeric bushing according to the invention, the supporting webs have a varying radial height in the circumferential direction. For example, at least one support bar has a radial height that varies in the circumferential direction. For example, the radial height of the at least one support web, in particular all the support webs, decreases towards an open end section of the half-shell and/or towards an apex of the half-shell, in particular continuously. It has been found that lower radial loads occur in the area of the 3/9 o'clock position and also the 6 o'clock position, so that material can be saved in these areas in order to reduce the rigidity in this regard.

According to a further exemplary embodiment, the supporting webs have, in particular, a concave recess in the region of a vertex of the c-shaped half-shells. In other words, the recess is at the 6 o'clock position. In the mounted state in the elastic mount, the recess points downwards in the vertical direction.

In a further exemplary embodiment of the elastomer bush according to the invention, one half-shell has greater radial rigidity transversely to the longitudinal axis than the other half-shell. For example, the stiffness difference between the two half-shells is between 0.1% and/or at most 5%.

According to another aspect of the present invention, consistent with the foregoing Aspects and exemplary embodiments can be combined, an elastic bearing, in particular a decoupling bearing, is provided for mounting a drive train component, in particular a transmission, of a wind turbine, in particular on its housing, such as its machine carrier. For example, it is an elastic bearing of a gear on a housing, such as a machine support, a wind turbine. Resilient mounts are used in wind turbines to absorb the dynamic loads acting on the drive train component and housing. Oscillation and/or vibration damping and decoupling can take place by means of the elastic mount. With regard to the basic installation situation of the elastic bearing, see EP 2 516 883 referenced, the relevant content of which is incorporated by reference into the present application.

The elastic bearing according to the invention comprises an elastomeric bushing designed according to one of the exemplary aspects or exemplary embodiments described above and two bearing block parts for receiving the elastomeric bushing in particular in a clamping manner. The bearing block parts are to be arranged or arranged on the housing side and are decoupled or damped from one another by the elastic bearing with regard to oscillation and/or vibration. For this reason, the elastic mount can also be referred to as a decoupling mount.

According to a further aspect of the present invention, which can be combined with the preceding aspects and exemplary embodiments, an elastic bearing, in particular a decoupling bearing, is provided for mounting a drive train component, in particular a transmission, of a wind turbine, in particular on its housing, such as its machine carrier. For example, it is an elastic bearing of a gear on a housing, such as a machine support, a wind turbine. Resilient mounts are used in wind turbines to absorb the dynamic loads acting on the drive train component and housing. Oscillation and/or vibration damping and decoupling can take place by means of the elastic mount. With regard to the basic installation situation of the elastic bearing, see EP 2 516 883 referenced, the relevant content of which is incorporated by reference into the present application.

The elastic bearing according to the invention comprises an elastomeric bushing designed in particular according to one of the exemplary aspects or exemplary embodiments described above and two bearing block parts for receiving the elastomeric bushing in particular in a clamping manner. The elastomeric bushing comprises two half-shells, each made from a piece of elastomer with a Shore hardness greater than 85 Shore A. According to this aspect, the elastomer bushing is designed in such a way that an axial play of movement of the elastomer bushing in the direction of its longitudinal axis relative to the bearing block parts or relative to a fastening part that may be accommodated by the elastomer bushing, such as a torque support or an axle bolt, of the drive train component under a load, in particular in the longitudinal direction , to which the elastic bearing is admitted. For example, the axial play is at least 1mm and at most 50mm, in particular between 1mm and 40mm, 30mm, 20mm or 10mm. An axial play in the range of 2mm to 3mm has proven to be advantageous.

The elastomer bushing can also be set up and/or dimensioned in such a way that there is less relative movement play transverse to the longitudinal axis, in particular in the radial direction, relative to the bearing block parts or relative to a fastening part, such as a torque support or an axle bolt, of the drive train component that may be accommodated by the elastomer bushing than the axial relative movement play, in particular is prevented.

According to a further aspect of the present invention, which can be combined with the preceding aspects and exemplary embodiments, a wind power plant is provided with an elastic bearing according to one of the aspects described above.

Preferred embodiments are specified in the dependent claims.

• 1 eine perspektivische Ansicht einer beispielhaften Ausführung einer Halbschale einer erfindungsgemäßen Elastomerbuchse;
• 2 eine Vorderansicht der Halbschale nach 1;
• 3 eine Seitenansicht der Halbschale gemäß 1 bzw. 2;
• 4 eine perspektivische Ansicht einer Halbschale einer weiteren beispielhaften Ausführung einer erfindungsgemäßen Elastomerbuchse;
• 5 eine Vorderansicht der Halbschale nach 4;
• 6 eine Seitenansicht der Halbschale gemäß der 4 bzw. 5;
• 7 eine perspektivische Ansicht einer Halbschale einer weiteren beispielhaften Ausführung einer erfindungsgemäßen Elastomerbuchse;
• 8 eine Vorderansicht der Halbschale nach 7;
• 9 eine Seitenansicht der Halbschale gemäß 7 bzw. 8;
• 10 eine Seitenansicht einer beispielhaften Ausführung eines erfindungsgemäßen elastischen Lagers;
• 11 eine Schnittansicht des elastischen Lagers nach 10; und
• 12a - 12f schematische Schnittdarstellungen zur Veranschaulichung der Montage eines elastischen Lagers gemäß der vorliegenden Erfindung.

In the following, further properties, features and advantages of the invention are made clear by means of a description of preferred embodiments of the invention using the accompanying exemplary drawings, in which:

• 1 a perspective view of an exemplary embodiment of a half-shell of an elastomeric bushing according to the invention;
• 2 a front view of the half shell 1 ;
• 3 according to a side view of the half-shell 1 or. 2 ;
• 4 a perspective view of a half-shell of a further exemplary embodiment of an elastomeric bushing according to the invention;
• 5 a front view of the half shell 4 ;
• 6 a side view of the half-shell according to FIG 4 or. 5 ;
• 7 a perspective view of a half-shell of a further exemplary embodiment of an elastomeric bushing according to the invention;
• 8th a front view of the half shell 7 ;
• 9 according to a side view of the half-shell 7 or. 8th ;
• 10 a side view of an exemplary embodiment of an elastic bearing according to the invention;
• 11 a sectional view of the elastic bearing 10 ; and
• 12a - 12f schematic sectional views to illustrate the assembly of an elastic bearing according to the present invention.

Based on 1 until 9 three exemplary embodiments of elastomeric bushings according to the invention, generally designated by the reference number 1, are described. In the 1 until 9 a half-shell, which is generally provided with the reference number 3, of the respective elastomeric bushing 1 is shown in each case. It can be assumed here that the second half-shell 3 ′ ( 10 ) can have essentially the same structure. In this respect, the statements made in relation to the half-shell 3 shown can be applied to the second, in the 1 until 9 not shown, half-shell 3 'are transferred. Based on 10 until 12f exemplary embodiments of an elastic bearing according to the invention, which is generally provided with the reference numeral 5, are described in more detail, with reference to FIG 12a until 12f the assembly of the elastic bearing 5 is illustrated. For the following description of the exemplary embodiments shown in the figures, it can be assumed that the half-shell 3 of the elastomer bushing 1 is made from an elastomer piece with a Shore hardness of more than 85 Shore A, with the material polyurethane preferably being used.

Referring to the first exemplary embodiment of a half-shell 3 of an exemplary embodiment of an elastomeric bushing 1 according to the invention 1 until 3 the basic structure of the half-shell 3 can be seen. The half-shell 3 has a semi-circular shape in cross section. The half-shell 3 has a cross section that is constant in sections in the direction of longitudinal extent, that is to say along the longitudinal axis A. The half-shell 3 is curved in a concave manner and has an open side which is to be assigned and turned toward the second half-shell 3' (not shown).

The half-shell 3 delimits a semi-cylindrical, hollow inner space 7, which serves to receive a connecting part of the drive train component (not shown), such as a torque arm (axle bolt 9 in see 10 ). An inner wall 11 of the half-shell 3 delimiting the interior space 7 is evenly curved along the longitudinal axis A and extends from a front-side, semi-cylindrical opening 13 to an opposite front-side, semi-cylindrical opening 15, so that, for example, the axle bolt 9 protrudes from the half-shell 3 on both front sides can.

In the area of an open end section 15 of the half-shell 3, the half-shell 3 has flat bearing surfaces 19, 21 extending in the direction of the longitudinal axis A, which come into contact with, in particular, complementary-shaped bearing surfaces of the further half-shell (not shown) when installed in the elastic bearing 1. In the area of the end section 17 there is also a radial projection 23 which projects transversely to the direction of the longitudinal axis A over an outer circumference of the half-shell 3 and forms an anti-twist device in the elastic bearing 1 . The anti-twist device is secured by means of the radial projection 23 by form-fitting engagement in a corresponding depression in the associated bearing block parts 25, 27 ( 10 ) of the elastic bearing 1 or by arranging the radial projection 23 in the assembled state in the elastic bearing 1 in such a way that relative rotation of the elastomer bushing 1 relative to the bearing block parts 25, 27 surrounding the half-shells 3 is avoided. For example, the radial projection 23 can be arranged in the contact or separation area between the two bearing block parts 25, 27, and in particular can be clamped by the bearing block parts 25, 27.

The half-shell 3 has an axial rigidity that varies in the direction of its longitudinal axis A and a radial rigidity that varies transversely to the longitudinal axis A. The half-shell 3 has in the 1 until 3 three support webs 29 arranged at a distance from one another in the direction of the longitudinal axis A, in particular of identical design, which extend away from an outer circumference 31 transversely to the direction of the longitudinal axis A, in particular in the radial direction, and protrude from the outer circumference 31. A groove 31 oriented in the circumferential direction and forming an escape space is formed between each two adjacent support webs 29 . The support webs 29 can be dimensioned and/or curved in the circumferential direction in such a way that a radius of curvature of an imaginary outer contour line of the support webs 29 den has the same radius of curvature as the outer circumference 31.

In the 1 until 3 three axial support webs 30 are provided, which form two grooves 33 between them. When a load or force is applied from the outside, in particular in the direction of the longitudinal axis A, on the elastomer bushing 1 or the half-shell 3, the axial support webs 30 can, in particular, yield elastically into the adjacent grooves 33 or deform in such a way that the axial support webs 30 at least partially fill the grooves 33 . The deflection of the axial support webs 30 into the adjacent grooves 33 has the effect, on the one hand, that the half-shell 3 has a lower axial rigidity with respect to the radial rigidity. Furthermore, the variation of the axial rigidity in the direction of the longitudinal axis A is to be understood in such a way that the half-shell 3 can have a varying radial wall thickness along the longitudinal axis A. In the event of an external load, particularly in the operating state in the mounted elastic bearing 5, the axial support webs 30 can deviate into the adjacent grooves 33, so that relative movement play between the elastomer bushing 1 and the two bearing block parts 25, 27 or, if applicable, the axle bolt 9 in the longitudinal direction A is permitted. As in the 1 until 3 can be seen, the half-shell 3 is mirror-symmetrical with respect to a center plane M. The axial support webs 30 have, as is particularly the case in 2 can be seen, an essentially rectangular cross-sectional shape, so that the adjacent escape grooves 33 essentially have a trapezoidal shape ( 2 ).

In particular from the 1 and 2 it can be seen that the support webs 29 are segmented in the circumferential direction. This means that the support webs 29 are divided into circumferential support webs 35 in the circumferential direction. When executed according to 1 until 3 four circumferential support webs 35, in particular of the same dimensions, are formed per support web 29. The peripheral support webs 35 are designed to deviate in the peripheral direction into an adjacent recess 37, 39 forming an escape space when a load is applied, in particular in the direction of the longitudinal axis A. In particular from 2 shows that a substantially central recess 37 is dimensioned larger in the circumferential direction than the two adjacent recesses 39. In this respect, a deformation possibility of the circumferential support webs 35 adjoining the central recess 37 is greater than a deformation possibility of the two outer circumferential support webs delimiting the narrower recesses 39 35. In general, it is clear that a supporting web section can be a circumferential supporting web as well as an axial supporting web. This is the case in particular when the support webs 29 are segmented both in the axial and in the circumferential direction.

The execution of the half-shell 3 of 4 until 6 Another exemplary elastomer bushing 1 according to the invention differs from the embodiment according to FIG 1 until 3 essentially through the realization of the varying axial and/or radial rigidity. For the rest, reference can be made to the previous statements.

As from a comparison of 4 until 6 with the 1 until 3 shows is in the execution according to the 6 the mechanism for enabling the axial relative movement play between the elastomer bushing 1 and the further component, namely the fastening part of the drive train component, such as the axle bolt 9, is arranged on the inner circumference or on the inner wall 11. The outer circumference 31 is designed to be continuous and essentially forms a cylindrical outer contour. When executing the 4 until 6 7 supporting webs 41 are arranged on the inside in the region of the interior. The inner support webs 41 are segmented or subdivided both in the axial and in the radial direction to form circumferential support webs 45 and to form axial support webs 42 . The axial support webs 42 extend essentially in the direction of the longitudinal axis A and protrude radially inwards from the inner circumference 11 into the interior space 7 . A groove 43 forming an escape space is formed between each two adjacent axial support webs 42 . Analogously to the functioning of the outside support webs 29, in particular the outside axial support webs 30, the inside axial support webs 42 can deviate into the respective adjacent inside groove 43 in the event of an external load, in particular in the direction of the longitudinal axis A, on the elastomer bushing 3. According to 4 It can be seen that in the exemplary embodiment, two axial support webs 42 are provided which are arranged at a distance from one another in the direction of the longitudinal axis A and delimit an alternative groove 43 which is arranged in particular in the center with respect to the longitudinal extension of the half-shell 3 and which essentially runs all the way round in the circumferential direction.

Furthermore, according to the configuration of the outside support webs 29, the inside support webs 41 are divided in the circumferential direction into circumferential support webs 45, for example into three circumferential support webs 45. In this respect, between each two adjacent circumferential support webs 45 there are essentially straight cutouts 47 extending in the direction of the longitudinal axis A, into which, in turn, the peripheral support webs 45 can deviate when a load and/or force is applied from the outside. The circumferential support webs 45 have a substantially constant cross-section in the direction A of the longitudinal axis. The same applies to the adjacent alternative recesses 47.

Referring to the 7 until 9 is an embodiment of a half-shell 3 shown as a combination of the design and structural features of the half-shells of the two versions of the 1 until 3 or. 4 until 6 is to be understood. This means that the half-shell 3 according to the 4 until 6 has both the inside play mechanism and the outside play mechanism in both the axial and radial directions. With regard to the respective structural details, reference can be made to the previous description. The half shell 3 of 7 until 9 therefore makes it possible that when a load is applied, in particular in the longitudinal direction A, on the elastomeric bushing 1 in its mounted state in an elastic bearing 5, the elastomeric bushing 1 can move axially in the longitudinal direction A both relative to the outside bearing block parts 25, 27 and relative to the inside axle bolt 9.

Referring to the 10 and 11 an exemplary embodiment of an elastic bearing 5 according to the invention is shown. 10 shows an assembly state of the elastic bearing 5 from the side. In the middle, on the inside, there is a fastening part designed as an axle bolt 9 of a drive train component, for example a gearbox of the wind turbine, which is bordered and surrounded on the outside by an elastomer bushing 1 according to the invention, for example. The elastomeric bushing 1 is in turn surrounded or bordered by two bearing block parts 25, 27, which are to be understood on the wind turbine side.

The bearing 5 according to the invention, which can also be referred to as a decoupling bearing if it is designed in such a way that it can decouple oscillations and/or vibrations between the drive train component and the housing of the wind turbine, serves to attach the drive train component to the housing of the wind turbine, in particular its To store machine carrier, vibration-decoupling and/or vibration-damping. Namely, by means of the elastomer bushing 1 in particular according to the invention, oscillation and/or vibration damping and/or decoupling between the components mentioned is made possible. In the assembled condition as shown in 10 is shown, it is possible that the elastomer bushing can perform an axial relative movement play in the direction of its longitudinal axis A and/or a radial relative movement play transverse to the longitudinal axis A relative to the bearing block parts 25, 27 or the axle bolt 9 when there is an external load on the elastic bearing.

In 11 FIG. 14 is a sectional view of the elastic mount 1. FIG 10 shown. the end 11 It can be seen that the axle bolts 11 extend to a front side 49 of the bearing beyond the front side 49, namely up to the drive train component, which is not shown. On the opposite end face 51, the axle bolt is flush with the bearing block parts 25, 27. the end 11 it can also be seen that the axial dimensioning of the elastomer bush, in particular its half-shells 3, is less than the axial dimensioning of the bearing block parts 25, 27.

When assembling the elastic bearing 5 according to the invention, a half-shell 3 of the elastomer bushing 1 is first inserted between the two bearing block parts 25, 27, in particular on the lower bearing block part 25 ( 12a) . Then the fastening part of the drive train component, here the axle bolt 9, is also pushed into the bearing space 53 delimited by the bearing block parts 25, 27 ( 12b) . the end 12b it can be seen that the center point M ₃ of the lower half-shell 3 is offset from one another, in particular in the vertical direction, with respect to its center point M ₃ of the axle bolt 9 . The axle bolt 9 is then removed in the vertical direction and placed on the lower half-shell 3 . The result is a significantly smaller center offset between the axle bolt 9 and the lower half-shell 3 ( 12c ). Then the axle bolt 9 and the lower half-shell 3 are aligned to one another as far as possible, in particular centered relative to one another, so that there is only a slight center offset (in 12d not shown). The center points M ₃ and M ₉ are aligned with one another by pretensioning or bracing the lower half shell 3 . After the lower half shell 3 has been pretensioned, the second half shell 3 , in particular the upper half shell 3 ′, can be inserted into the storage space 53 . As in 12e is indicated, there is a slight center offset, particularly oriented in the vertical direction, between the axle bolt 9 or the lower half-shell 3 and the upper half-shell 3'. By finally relaxing the elastic bearing 5, the two half-shells 3, 3' and the axle bolt 9 can be aligned with one another, so that there is essentially no longer a center offset ( 12f) . Axle bolts 9, lower and upper half-shells 3, 3' are arranged essentially concentrically to one another. This results in an elastic bearing 1 that is as space-saving as possible.

The features disclosed in the above description, the figures and the claims can be important both individually and in any combination for the implementation of the invention in the various configurations.

Reference List

1

elastomer bushing

3

half shell

5

elastic bearing

7

inner space

9

axle bolt

11

inner wall

13:15

frontal opening

17

open end section

19:21

bearing surface

23

radial protrusion

25, 27

bearing block part

29

external support bar

30

External axial bearing web

31

outer perimeter

33

groove

35

External perimeter support bar

37, 39

recess

41

inner support bar

42

Inner axial bearing web

43

groove

45

Inner Circumferential Wear Bar

47

recess

49, 51

face

A

longitudinal axis

M

central axis

wed

center of a component i

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• EP 2516883 [0003, 0006, 0012, 0025, 0027]

Claims (17)

Elastomeric bushing (1) for an elastic bearing (5) of a drive train component of a wind power plant, in particular a gearbox on a housing, such as a machine carrier, of a wind power plant, comprising two half-shells (3, 3'), each made of an elastomer piece with a Shore hardness of more than 85 Shore A, at least one half-shell (3, 3') having an axial rigidity that varies in the direction of its longitudinal axis. Elastomer bushing (1) after claim 1 wherein at least one piece of elastomer comprises polyurethane, in particular polyurethane-polyester or polyester-urethane rubber, preferably Urelast. Elastomer bushing (1) after claim 1 or 2 , wherein the half-shells (3, 3') each have a central axis which is oriented concentrically to one another when the half-shells rest on one another and/or in the assembled state in the elastic bearing, in particular in the operating state. Elastomer bushing (1) according to one of the preceding claims, whose radial stiffness transversely to the longitudinal axis is greater than its axial stiffness in the direction of the longitudinal axis, the axial stiffness in particular being less than 10%, in particular less than 5% or in the range of 2% to 3%, of the radial stiffness . Elastomeric bushing (1), in particular according to one of the preceding claims, for an elastic bearing (5) of a drive train component of a wind turbine, in particular of a transmission on a housing, such as a machine carrier, of a wind turbine, comprising two half-shells (3, 3'), each are made from an elastomer piece with a Shore hardness of more than 85 Shore A, with at least one half-shell (3, 3'), in particular the half-shell with the varying axial rigidity, at least two at a distance in the longitudinal direction and/or transversely, in particular vertically , has supporting webs (29, 41) arranged towards one another, which protrude from an outer or inner circumference of the half-shell in such a way that an escape space, in particular a groove (37, 39), is formed between each two supporting webs (29, 41). Elastomer bushing (1) after claim 5 , wherein the support webs (29, 41) are set up to deviate in the event of a load, in particular in the longitudinal direction and/or transversely thereto, onto the elastomer bushing (1) in the longitudinal direction and/or transversely thereto into an adjacent escape space. Elastomeric bushing (1) according to one of Claims 5 or 6 , wherein the support webs (29, 41) are rectangular in cross-section or have a conical shape and/or in particular taper continuously in the radial direction. Elastomeric bushing (1) according to one of Claims 5 , 6 or 7 , wherein at least one support web (29, 41) is segmented in the circumferential direction, in particular in such a way that at least 2, 3 or 4 circumferential support webs (35, 45) are formed, with in particular two adjacent circumferential support webs (35, 45) in the circumferential direction of one, in particular rectilinear and/or longitudinally oriented recesses (37, 39, 47) are separated from one another. Elastomer bushing (1) after claim 8 , the peripheral support webs (35, 45) being set up to deviate in the peripheral direction into an adjacent recess (37, 39, 47) in the event of a load, in particular transverse to the longitudinal direction, on the elastomer bushing (1). Elastomeric bushing (1) according to one of the preceding claims, wherein at least one half-shell (3, 3') has an anti-twist device which is realized by pinning, gluing or by a radial projection interacting with a bearing block part of the bearing. elastomeric bushing (1) claim 10 , wherein the half-shells (3, 3 ') have a c-shaped cross-section and the radial projection is arranged in the region of an open end of the c-shaped cross-section. Elastomeric bushing (1) according to one of the preceding claims, wherein at least one half-shell (3, 3') has a radial rigidity which varies transversely to the longitudinal axis. Elastomer bushing (1) after claim 12 , wherein the supporting webs (29, 41) have a varying radial height in the circumferential direction, the radial height of the supporting webs (29, 41) in particular decreasing towards an open end section of the half-shell (3, 3'). Elastomeric bushing (1) according to one of the preceding claims, wherein the supporting webs (29, 41) have a particularly concave recess (37, 39, 47) in the region of an apex of the c-shaped half shells (3, 3'). Elastomeric bushing (1) according to one of the preceding claims, wherein one half-shell (3, 3') has greater radial rigidity transversely to the longitudinal axis than the other half-shell (3', 3). Elastic bearing (5), in particular a decoupling bearing, for mounting a drive train component, in particular a transmission, a wind turbine, in particular on its housing, such as a machine carrier, comprising an elastomer bushing (1) designed according to one of the preceding claims and two bearing block parts (25, 27) for in particular by jamming the elastomer bushing (1). Elastic bearing (5), especially after Claim 16 , In particular decoupling bearings, for storing a drive train component, in particular a transmission, a wind turbine in particular on its housing, such as a machine carrier, comprising a particular according to one of Claims 1 until 15 formed elastomer bushing (1) with two half-shells (3, 3'), each made of an elastomer piece with a Shore hardness of more than 85 Shore A, and two bearing block parts (25, 27) for receiving the elastomer bushing (1 ), wherein the elastomeric bushing (1) is designed in such a way that an axial play of movement of the elastomeric bushing (1) in the direction of its longitudinal axis relative to the bearing block parts (25, 27) or relative to a fastening part that may be accommodated by the elastomeric bushing (1), such as a Torque support or an axle bolt (9), the drive train component is allowed to act on the elastic bearing (5) when a load is applied, in particular in the longitudinal direction, with the axial play of movement being at least 1 mm and at most 50 mm, in particular in the range from 2 mm to 3 mm.

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